Balling head



July 3, 1962 c. .1. HAUG ET AL 3,042,330

BALLING HEAD Filed June 22, 1959 5 SheetsSheet 1 L} I In" I FIG.|

lNVE NTORS CHESTER J. HAUG GEORGE S. VAN DEUSEN BY JACK H. SELBY July 3,1962 c. .1. HAUG ET AL 3,042,330

BALLING HEAD Filed June 22, 1959 5 Sheets-Sheet 2 \NVENTORS CHESTER J.HAUG GEORGE s. VAN DEUSEN BY JACK H. SELBY July 3, 1962 c. J. HAUG ETALBALLING HEAD 5 SheetsSheet 5 Filed June 22, 1959 FIG.3

\NVENTORS CHESTER J. HAUG GEORGE S VAN DEUS'EN JACK H. SELBY 7464M,

July 3, 1962 c. .1. HAUG ET AL 3,042,330

BALLING HEAD Filed June 22, 1959 5 SheetsSheet 4 INVENTORS F G 5 CHESTERJ. HAUG GEORGE S. VAN DEUSEN BY JACK H. ELBY A 7' roe/vars July 3, 1962c. J. HAUG ET AL BALLING HEAD 5 Sheets-Sheet 5 Filed June 22, 1959INVENTORS N I AUW W HE ie .D 1

Ns m WM f g e 4 E I. HE

United States Patent 3,042,330 BALLING HEAD Chester J. Haug, Cleveland,George S. Van Deusen,

Lyndhurst, and Jack H. Selby, Chagrin Falls, Ohio,

assignors to The Warner & Swasey Company, Cleveland, Ohio, a corporationof Ohio Filed June 22, 1959, Ser. No. 821,938 3 Claims. (Cl. 242-544)This invention relates to a balling head mechanism such as is used withcarding machines, gill boxes and other similar machines to wind sliverof textile fibers into ball-like packages.

When sliver is being wound onto a ball, the mechanism which handles thesliver may exert an uneven tension at certain times during operation byvirtue of a change in the path length of the sliver. Since slivercomposed of the usual textile fibers is relatively fragile, any tensionbeyond a certain minimum tends to draft the fibers and lessen the weightof the sliver at that point. The resulting unevenness is veryundesirable for its presence during the early stages of fiberpreparation may mean that additional gilling and doubling operationswill be required. The occurrence of such unevenness in the final gillingoperations usually means that an inferior yarn will be produced.

The use of ball type sliver packages has many advantages for purposes ofstorage, dyeing, and handling but balls have found little use beyond theinitial operations because of the problems of forming the balls at thehigh speeds of modern gilling, carding and combing machines withoutintroducing objectional unevenness in the sliver.

Therefore, an object of this invention is to provide a novel ballinghead mechanism which maintains a relatively constant sliver path lengthat all times during balling without any drafting effect on the sliver.

Another object of the invention is to provide a balling head mechanismhaving a compensating device for maintaining constant sliver path lengthbetween the calender rolls and twister trumpet regardless of thetraverse position of the crosshead and which is easily adjustable asrequired for various fibers and sliver weights.

Another object of the invention is to provide in a balling headmechanism a compensating device for maintaining constant sliver pathlength, to enable constant tension to be maintained, which isself-contained with the crosshead and traversing mechanism.

Another object of the invention is to provide in a balling headmechanism a traverse drive which produces a compact, symmetrical ballhaving a uniform diameter and square ends.

A further object of the invention is to provide a balling head mechanismhaving a minimum of reciprocating mass to allow operation at high speedswith a minimum of power and wear and which is readily adjustable as toball length, traverse rate, and ball density.

Still another object of this invention is to provide a novel ballinghead mechanism capable of producing a large ball yet requiring a minimumof floor space and having a relatively simple construction.

Further and additional objects and advantages of the invention willbecome apparent from the following detailed description and accompanyingdrawings which show one embodiment of the invention as used incombination with a gill box, although it is understood that it may alsobe used in combination with other types of machines which produce sliveror a sliver-like material as a product.

In the drawings:

FIG. 1 is a perspective view of a gill box and creel 3,@4Z,330 PatentedJuly 3, 1962 provided with a balling head embodying the presentinvention;

FIG. 2 is a front elevational view of the balling head shown in FIG. 1,but with certain parts broken away to better show the traverse drive;

FIG. 3 is a side elevatioual view with covers removed showing the drivemechanism to the drive roll and traverse mechanism.

FIG. 4 is a sectional view taken on line 4-4 of FIG. 2 looking in thedirection of the arrows;

FIG. 5 is a developed sectional view of the drive mechanism taken alonga broken plane from center to center of the various shafts but withparts rotated from the position of FIG. 4 to facilitate the showing ofthe parts;

FIG. 6 is a sectional view taken on line 66 of FIG. 2 and showing thetraverse arm, crosshead. and compensating arm;

FIG. 7 is a sectional view taken along line 77 of FIG. 6 and showing themounting of the compensating arm; and

FIG. 8 is a schematic view showing the method of adjusting the stroke ofthe traverse arm.

Referring now to the figures in detail, FIG. 1 shows the balling head,indicated generally at 10, attached to the front of a gill box 11. Thegill box may be constructed in the usual manner and is supplied withsliver ends 12 taken from supply balls 13 mounted in creel 14. Thesliver ends 12 are delivered to the faller section 15 of the gill boxwhere they are combined and drafted in the manner well understood in theart, the finished sliver 17 emerging from the nip rolls 16. From the niprolls the sliver passes between a pair of upper and lower calender rolls18, 20, and then to the balling head 10 where it is formed into a bill10 The calender rolls 18, 20 are mounted on a bracket 19 attached to thefront of the gill box 11, and the lower calender roll 20 is journaled inthe bracket 19 and has an extension shaft portion 21 (see also FIG. 2)on the end of which is secured a sprocket 22 which is driven from thenip rolls 16. In practice, the lower calender roll 20 is driven at thesame angular "elocity as the nip rolls but is slightly larger indiameter to have a slightly greater surface speed so that no slack willdevelop in the sliver between the nip rolls and the calender rolls. Tokeep the sliver from slipping on the lower roll, the upper calender roll18 is journaled in a movable bracket 24 which is resiliently mounted tohold the upper roll 18 in contact with the sliver passing over lowerroll 20. Further description of the gill box and calender rolls is notdeemed necessary as they form no part of the present invention and areshown and described only to show equipment with which the ballingmechanism may be used.

The balling head mechanism, shown in greater detail in FIG. 2, has apair of upright frame members 30 and 31 which are spaced apart at thebottom by a cross beam 32. When used with a gill box, it may be attachedthereto by means of mounting plates 33 which are fastened both to thebacks of the upright frame members 30 and 31 and to the frame of thegill box.

From the calender rolls 18, 20, the ball of sliver is wound on an arbor34 which is freely rotatably journaled' at one end on one end of anarbor arm 35 and extends substantially perpendicularly to the arm. Theother end of arbor arm 35 is journaled on a shaft 36 which is pinned toa forked bracket 37 mounted on the front of upright frame member 30. Theaxes of the arbor 34 and shaft 36 are parallel to each other and to adrive roll 38 which is journaled at each end in the frame members 30 and31 and is disposed below the arbor 34. The sliver from the calender rollforms a ball on the arbor 34 and the ball is rotated by contact with therotating drive roll 38. When there is no ball on the arbor 34, it restson top of the drive roll 38 and as the ball builds up thereon, the arm35 swings about the shaft 36 to raise the arbor 34 and accommodate theball.

To insure that the ball will be built up evenly, the sliver must betraversed lengthwise of the arbor to move from side to side across theface of the ball during winding. The traversing of the sliver isaccomplished by a crosshead 39 through which the sliver passes and whichis slidably mounted on rails 40 and 41 for movement parallel to the axesof the drive roll 38 and arbor 34, the rails being supported between theuprights 3t 31. The crosshead 39 is reciprocated along the rails to movethe crosshead and sliver back and forth across the ball by anoscillating traverse arm 42 as explained more fully hereinafter.

The drive for the balling head mechanism which rotates the drive roll 38and oscillates the traverse arm 42 is shown in detail in FIGS. 2 through5. As stated above, the lower calender roll 20 is driven from the gillbox through a chain drive to sprocket 22 on extension shaft 21. Theshaft 21 also carries another sprocket 43 which drives a chain indicatedat 44 which, in turn, drives a sprocket 45. The sprocket 45 is securedon a gear 46 journaled on stub shaft 47 secured in frame member 31. Anidler gear 48 mates with the gear 46 and a driven gear 51 is mounted ona stub shaft 49 which is adjustably secured in an arcuate slot 50 inframe member 31. This adjustment does not change the engagement betweengear 46 and idler gear 48, but allows the use of different sized gearsfor driving the drive roll gear 51 which is keyed to a shaft portion 52of the drive roll 38 to effect rotation of the drive roll. By varyingthe number of teeth on drive roll gear 51, the surface speed of thedrive roll 38 will be varied with respect to that of the lower calenderroll 20. The drive roll is driven with a surface speed slightly greaterthan that of the lower calender roll 20, the exact amount depending uponthe nature of the sliver, to give the ball the necessary compactness.

Also keyed on shaft portion 52, between driven gear 51 and frame member31, is a drive gear 53 from which the drive to the traverse arm istaken. An idler gear 54 is driven by drive gear 53 and is mounted on astub shaft 55 which is adjustable in a second arcuate slot 56 in framemember 31 in a manner similar to the mounting of idler gear 48. Theidler gear 54 meshes with a driven gear 58 removably fixed to a shaft 57journaled in frame member 31. By substituting gears on the shaft 57 withdifferent numbers of teeth, the rate of traverse of the traverse arm 42and crosshead 39 can be varied relative to the speed of the drive roll38.

A bracket 63 is fastened to the inside of the frame member 31 adjacentthe shaft 67 and is spaced away therefrom to support part of a doublecrank or fast motion mechanism. This mechanism is incorporated into thedrive from the shaft 57 to the traverse arm to reduce the amount ofdwell at each end of the traverse, as explained in greater detailhereinafter. Shaft 57 passes through frame member 31 into the spaceadjacent to the bracket 63 and on its inner end carries a crank arm 59.A roller 60 is secured on the projecting end of crank arm 59 and isreceived in a slot 61 of a crank yoke 62, journaled on a stub, shaft 64secured in bracket 63 and having an axis parallel to the shaft 57.

The axis of stub shaft 64 is offset from the axis of shaft 57 toward thefront of the machine and therefore the yoke 62 and crank 59 rotate aboutoffset axes. The amount of the offset is a small portion of the spacingof the axis of the roller 60 on the end of crank 62 from the axis ofshaft 57. The drive train, as described hereinabove, rotates shaft 57and crank arm 59 at a uniform velocity, and since the roller 60 is fixedon crank arm 59, the roller will move in a circular path at a constantvelocity. However, since the axis of crank yoke 62 is displaced from thecenter of the circle described by roller 60, and since the point ofcontact where roller 60 rotates the crank yoke 62 must lie on theaforesaid circle, which is eccentric with respect to the axis of stubshaft 64, the crank yoke 62 is rotated by a lever arm of varyingeffective length. When the effective lever arm of crank yoke 62 is theshortest, as is shown in FIG. 5, it is rotated at an angular velocitygreater than that of the crank arm 59, and conversely, when theeffective lever arm is the longest, as is shown in FIG. 4, the crankyoke 62 has an angular velocity less than that of crank arm 59. In onerevolution, the angular velocity of the crank yoke 62 varies from amaximum to a minimum and back to a maximum during one revolution, butthe number of revolutions of both the crank yoke and the crank armremain constant. Increasing the offset of the stub shaft 64 orshortening the lever arm of roller 60 will produce a greater variationbetween the maximum and minimum angular velocities, and vice versa.

The drive from this double crank mechanism to the traverse arm is takenfrom a gear 65 which is keyed on the shank portion of the crank yoke 62.An idler gear 66 meshes with the gear 65 and is journaled on a stubshaft 67 secured in the wall of bracket 63 by a nut 68. A jackshaft 69is journaled in a projecting support 70 on cross beam 32 and has a gear71 keyed to its one end and in mesh with the idler gear 66. The otherend of the jackshaft 69 has a bevel gear 72 keyed thereto which mesheswith a mating bevel gear 73 journaled on a stub shaft 74 secured in thewall of cross beam 32. A drive gear 75 is keyed on the shank of thebevel gear 73 and drives a traverse gear 76. The traverse gear 76 has anintegral shaft portion 77 which is journaled in the cross beam 32 by aroller bearing 78 and secured against axial movement by a locking collar79.

The mounting of the traverse arm 42 and its operative connection withtraverse gear 76 is best shown in FIGS. 2 and 6. The traverse arm 42 issecured at its lower end to a rocker shaft 80 by screws 81, the rockershaft 80 being journaled in cross beam 32 and secured against axialmovement by a lock collar 82. The traverse arm 42 has spaced from thelower end thereof a bore 83 wherein a shaft portion 84 of a drive yoke85 is journaled by a ball bearing 86. The drive yoke 85 has fixed to ita lug portion 87 which projects from it horizontally and transversely toportion 84 and hasat its outer end a pivotal connection 88with an idlerlink 89 whose lower end is fastened to a second rocker shaft 90journaled in cross beam 32 adjacent to but spaced from rocker shaft 80,and parallel thereto. From this it will be seen that a parallel ogramlinkage. is formed by the traverse arm 42, idler link 89, lug portion'87 of the drive yoke 85 and the cross beam 32, which serves to maintainthe drive yoke 85 in a fixed, non-rotating orientation duringoscillation of traverse arnr-42 about the axis. of the rocker shaft 80.The connection of the lug portion 87 to idler link 89 prevents freerotation of the yoke 85' on the axis of shaft portion 84 and relative tothe traverse arm 42.

The dn'veyoke 85 has a vertical groove or slot.91 in the face adjacentthe traverse gear 76. This slot receives a roller 92 which is secured on,a carrier plate 93 which in turn is fastened on the traverse gear 76.Roller 92 is positioned a suitable radial space outwardly from the axisof rotation of the traverse gear and is free to move vertically withinslot 91. As the traverse gear rotates, roller 92 thus oscillates thedrive yoke 85 in response to the hori zontal displacement of the rollerto rciprocate the traverse arm 42. Since the traverse arm 42 is in thevertical position whenever the roller 92 is in the same vertical planeas the axis of the traverse gear 76, it will be seen that the resultingoscillation of the traverse arm will be symmetrical with respect to thisvertical position, not only in position, but also in velocity. It shouldbe noted that in the disclosed drive, the traverse arm 42 isreciprocated from its mid or vertical position to a limit position inone direction and back to vertical position by 180 rotation of theroller 92 with the traverse gear 76 while a second 180 rotation in thesame direction moves the traverse arm 42 from its mid or verticalposition to a limit position and back to vertical position. In the caseof a crank and connecting rod type of drive, the connecting rod must beof infinite length to approach this result.

If traverse gear 76 were rotated at a constant angular velocity, thehorizontal displacement and velocity of roller 92 would be sinusoidal inform. In such case, the inherent characteristics of the sinusoidalmotion would result in a period of relatively slow movement effectivelyamounting to a dwell at each reversal of direction. Since the sliver isbeing wound on the ball at a constant rate, this slow up at eachreversal would result in a buildup of sliver to a larger diameter at theends of the ball. This objectionable build-up can be eliminated byreciprocating the crosshead 39 at a more nearly uniform velocity.

As stated hereinabove, the double crank mechanism has an outputcharacteristic wherein the output velocity varies from a maximum to aminimum and back during one complete revolution. The above-describeddrive by means of gears 65, 66 and 71, bevel gears 72 and 73 and gear'75 from the double crank mechanism to the traverse gear 76 results in atwo to one reduction in speed and the position of roller 92 with respectto crank yoke 62 is timed so that the point of maximum angular velocityoc curs when the traverse arm is reversing its direction of travel ateach end of the stroke. The point of minimum angular velocity of thetraverse gear 76 then occurs at the center of the stroke where a puresinusoidal motion would produce the maximum traverse velocity. Thus, theeffect of the double crank mechanism is to vary the rotational speed ofthe traverse gear to produce a more nearly uniform movement of thecrosshead while not aifecting the symmetrical nature of the motion.

The length of stroke of the crosshead 39 is adjusted by varying thestroke of the traverse arm 42, which, in tum, is done by changing theeffective lever arm of the roller 92. To this end, the carrier plate 93(see FIG. 8) is secured at one end on traverse gear 76 by a pivot bolt94. Roller 92 has a threaded shank 92a, which passes through the carrierplate and is secured by a nut 95 which fits within a clearance recess 96in the traverse gear. At the other end of the carrier plate 93, thereare a plurality of holes 97, which may be selectively brought intoalignment with one of several tapped holes 98 by rotating the carrierplate about the pivot bolt 94. The carrier plate 93 can then be lockedin the selected position by a bolt 99. It will be noted that the roller92 is located on the carrier plate 93 so that as it is shifted to andfrom the center of the traverse gear 76, by rotation of the carrierplate about the pivot bolt 94, the roller retains very closely the sameangular position on the traverse gear. Thus, for all lengths of thetraverse stroke, the timing of the double crank mechanism and thetraverse arm position remains effectively constant. To allow lubricationof the roller 92, a passage 100 connects the roller shank 92a with anelongated recess 101 in the carrier plate 93, which recess, in turn,connects with a passage 102 in the shaft portion 77 of the traversegear. Because some portion of the recess 101 will always register withthe passage 102 regardless of the position of the carrier plate 93, theroller 92 can be lubricated in a suitable manner through passage 102regardless of the stroke setting of the carrier plate,

As stated hereinabove, the crosshead 39 is slidably mounted on crossrails 40 and 41 which are secured at their ends to the frame members 30and 31. The lower rail 41 passes through a bore 103 in the lower part ofthe crosshead and ball bushings 104 (see FIG. 7) are disposed betweenthe rail and crosshead to facilitate its sliding movement, while a pairof plain bushings 105 (see FIG. 2) are disposed between the upper rail40 and the crosshead. The upper end of traverse arm 42 carries a roller106 which is received in a vertical slot 107 in the crosshead 39 toprovide the driving connection between the traverse arm and thecrosshead so that the oscillation of the arm 42 reciprocates thecrosshead along the rails 40, 41.

A twister 108 is journaled in the upper part of the crosshead just belowupper rail 40 by a pair of bushings 109 and 110 and is secured thereinagainst axial movement by a lock collar 111. The twister has a lower endadjacent the arbor 34 or the ball thereon and an axial bore 112 whichopens into a trumpet 113 at the upper end of the twister. The wall or"the twister adjacent its lower end has a cut out portion 114 and in thecenter of this cut out 114- a transverse bridge 115 is secured to fitacross the bore 112. As is well understood in the art, the sliver entersbore 112 through trumpet 113, passes over the bridge 115 and through thecut out portion 114 and leaves bore 112 at its lower end 116 adjacentthe drive roll 38 to be wound on the arbor 34. The purpose of thetransverse bridge 115 is to supply a certain amount of gripping force tothe sliver so that rotation of the twister can supply a false twist tothe sliver. To rotate the twister 103, the lower surface of upper rail40 is cut to form a rack 117 which engages a pinion gear 118 secured ontwister 108 between bushings 109 and 110. As the crosshead reciprocates,rack 117 will rotate pinion gear 118 and twister 103 first in onedirection and then in the other, but since the amount of these rotationsare equal, only a false twist is imparted to the sliver, as is wellunderstood in the art.

It will be seen that when the crosshead 39 is in the center position,trumpet 113 of twister 108 is directly beneath and at its closestdistance to the calender rolls 18, 20 and as the trurnpet is movedtoward either side, this distance necessarily increases because of theresulting angularity. Since the sliver comes out of the calender rollsat a constant rate, and since the sliver is drawn through the twister108 and wound on the ball at a constant rate, as this distance changes,the sliver length between the calender rolls and the trumpet mustnecessarily change. If the sliver is placed under the proper tension atthe shortest distance, then as the distance increases, the slivertension wil increase and usually result in a slight but definite andvery undesirable drafting of the sliver. Conversely, if the sliver isproperly adjusted at the traverse ends, at the center there will be aslack in the sliver which will interfere with proper forming of theball. This problem is accentuated by the increased angularity producedby a longer traverse width or by bringing the calender rolls and trumpetcloser together as must be done to produce a smaller and more compactmachine.

To eliminate this problem, the present balling head mechanism maintainsa constant path length for the sliver regardless of the position of thecrosshead. To this end, a compensating arm 120 is rotatably mounted atits lower end on a. pivot shaft 121 which is secured in a projecting lug122 of the crosshead 39. The compensating arm 120 extends upwards abovetrumpet 113 between the trumpet and the calender rolls 18, 20 and isprovided with a compensating sliver guide 123 around which the sliverpasses. At the lower end of the compensating arm 1 20 and disposed onthe side of shaft 121 remote from the upper end of the compensating armare a pair of projecting arms 124 between whose outer ends is attached acam follower bar or element 125 forming part of an inverse cammechanism. (See FIG. 2.) An element in the form of a driver roller 126is secured on the traverse arm 42 below roller 106 and includes aconical roller sleeve 127 which is contacted by the lower edge of camfollower bar or element 125. A double torsion or rat trap spring 128 hasits coiled portion mounted on bushings 129 on pivot shaft 121 and has alooped arm 130 which passes around compensating arm 120 while the othertwo arms 131 rest against the underside of crosshead 39 so that thespring rotates the compensating arm 120 to maintain cam follower bar orelement 125 in contact with roller sleeve 127 of the cam element on thetraverse arm 4-2.

When the crosshead is in the center of the traverse with the traversearm in the vertical position as shown in FIG. 6, the compensating arm istipped away from the crosshead and the sliver guide means carriedthereby. This is due to the roller 126 and sleeve 12'? being at thehighest point of their arcuate movement with the traverse arm 42. Topass around the compensating sliver guide 123, the sliver 132 must bendoutward around the guide and form effectively a bow or loop. As thetraverse arm 42 oscillates to either side of vertical position it movesthe crosshead toward either side from central position, the resultantangularity of the traverse arm lowers roller 126 and sleeve 127 formingthe cam element of the traverse arm away from the crosshead. The spring128 rotates the compensating arm toward the trumpet or sliver guidemeans on the cross head to maintain contact between cam follower bar orelement 125 and roller sleeve 127 of the traverse arm cam element sothat at the end of the traverse the compensating sliver guide is in theposition shown in dashed lines 1.33. By shortening the loop in thesliver produced by compensating sliver guide 123, the angularityproduced by the traverse of the crosshead is compensated for and theeifected sliver path remains constant at all times.

Because the loop formed at the center position must not only be of apredetermined length, but also must be taken up at a prescribed rateduring traverse to maintain constant sliver tension, the compensatingarm must follow a definite path, which needs to be adjustable fordifferent slivers. It can be seen that the angularity of the traversearm which lowers the driver roller 126 also causes the sleeve 127 toroll lengthwise along the lower edge of cam follower bar 125. By makingthis edge curved, the path of the sliver guide can be adjusted to thedesired shape. The same efiect can also be produced by varying theconical slope and diameter of sleeve 127, since rotation of thecompensating arm necessarily causes a relative movement between thefollower bar and sleeve along the axis of the sleeve.

Although only the preferred embodiment of the invention has been shownand described, it will be understood that various changes andmodifications to meet specific requirements can be made withoutdeparting from the scope of the invention as defined in the followingclaims.

Having thus described our invention, what we claim is:

1. In combination with a continuous textile sliver delivering mechanismhaving sliver exit means, a balling mechanism operatively associatedwith said delivering mechanism and comprising an arbor upon which thesliver is to be wound, means for rotating said arbor in timedrelationship to the operation of said delivering mechanism, a crossheadsupported for reciprocation in opposite directions from a centralposition and longitudinally of said arbor and provided with sliver guidemeans, the distance between said sliver guide means and said sliver exitmeans being shortest when the crosshead is in central position andvariably greater when said crosshead reciprocates therefrom, anoscillating traverse arm operatively connected to said crosshead, meansto oscillate said arm in timed relationship to said delivering mechanismto reciprocate said crosshead, and a sliver compensating mechanism formaintaining constant sliver length between said exit means and saidguide means and comprising a lever carried by said crosshead on the sidethereof that is toward said delivering mechanism and rockabletransversely of said crosshead on an axis parallel to said arbor, saidlever on one side of its pivotal connection being provided withcompensating sliver guide means located intermediate said exit means andsaid crosshead sliver guide means, said lever on the opposite side ofsaid pivotal connection having an actuating portion including a camelement, said traverse arm at a point spaced from said crossheadmounting a cam element cooperating with said first cam element, andspring means carried by said crosshead and acting on said lever tomaintain both of said cam elements in contact with each other wherebywhen said crosshead is in central position said compensating sliverguide means is located a maximum distance from the crosshead sliverguide means to provide a substantial bow in said sliver but when saidcrosshead reciprocates from. central position the arcuate movement ofthe traverse arm earn element lowers said element and said spring meansacts on said lever to rock the latter to move the compensating sliverguide means transversely of and toward said crosshead to positionscloser to the crosshead sliver guide means to reduce the magnitude ofsaid sliver bow in proportion to the increase in the distance betweensaid exit means and said crosshead sliver guide means.

2. The combination defined in claim 1 and wherein said traverse arm isvertically disposed and is pivotally mounted at its lower end while itsupper end is operatively connected to said crosshead, and said camelement that is carried by said traverse arm is spaced downwardly belowthe upper end of the traverse arm and said crosshead.

3. The combination defined in claim 1 wherein said lever of said slivercompensating mechanism is an L- shaped lever and its pivotal connectionto said crosshead is at the junction of the L-shaped portions of thelever while the compensating sliver guide means carried by the lever isat the upper end of the longer portion of the lever and the cam elementwhich cooperates with the cam element of the traverse arm is at the freeend of the actuating or shorter portion of the lever and said springmeans is a rat trap spring surrounding the pivotal axis of said leverand having its opposite ends respectively engaging the longer andshorter portions of said lever.

References (Iitetl in the file of this patent UNITED STATES PATENTS1,249,809 Noble Dec. 11, 1917 1,672,960 Stack lune 12, 1928 2,135,668Judelshon Nov. 8, 1938 2,950,068 Rutgers Aug. 23, 1960 FOREIGN PATENTS906,788 Germany Mar. 18, 1954 1,181,129 France Jan. 5, 1959

